Control mechanism

ABSTRACT

An energy storage mechanism for folding seats for vehicles and the like includes an energy-storing component such as a spring that assists in moving the seat or other component. The mechanism provides for relatively small user input forces and distances, yet provides a relatively large force acting over a relatively large distance as an output of the mechanism. The mechanism may be configured to provide for a single user input/release, without requiring powered actuators or the like.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of U.S. patent applicationSer. No. 11/843,422, filed on Aug. 22, 2007, which claims the benefit ofU.S. Provisional Application No. 60/839,217, filed on Aug. 22, 2006, andU.S. Provisional Application No. 60/885,135, filed on Jan. 16, 2007,both entitled STORED ENERGY CONTROL MECHANISM. The entire contents ofall of the above-identified applications are incorporated herein byreference.

BACKGROUND OF THE INVENTION

Various mechanisms for moving and/or folding seats for motor vehicleshave been developed. One type of seat that may be used in Sport UtilityVehicles (“SUVs”), vans or the like includes one or more mechanisms thatenable the seat back to be folded down, followed by upward and forwardrotation of the seat back and base. Such seats provide for increasedspace for transporting large objects or the like when the rear seats ofthe vehicle are not needed.

Although such seats have been widely used due to the need for increasedspace, known mechanisms may not fully assist the user in folding theseat. Thus, known folding seat arrangements may require substantialinput of force by a user to fold and/or unfold the seat.

Electrically-powered folding seats have also been developed, but theelectrical actuators and related electrical components tend to be morecostly than known mechanical mechanisms. Due to the added complexity,weight, and extra expense, powered folding seats have had somewhatlimited acceptance in the marketplace.

SUMMARY OF THE INVENTION

The present invention relates to an energy storage mechanism that can beutilized to assist in folding a vehicle seat. The mechanism may beutilized in a wide range of other applications as well. The mechanismmay include a cam that rotates to move cables that are, in turn,utilized to release a mechanism such as a latch, lock, or the like. Themechanism may be released by a relatively small user input force andmovement such as movement of a release lever or the like, yet providefor a relatively large output force acting over a relatively large rangeof movement. If the mechanism is utilized to assist in movement of avehicle seat to a folded position, the mechanism stores energy as theseat is folded downwardly to a use position, and releases the energy toassist in moving the seat from a use position to a folded position.

These and other features, advantages, and objects of the presentinvention will be further understood and appreciated by those skilled inthe art by reference to the following specification, claims, andappended drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partially schematic side view of a folding seat for vehiclesand the like including an energy storage mechanism according to oneaspect of the present invention;

FIG. 2 is a partially schematic side view of the folding seat of FIG. 1wherein the seat is in the folded configuration;

FIG. 3 is a cross-sectional view of an energy storage mechanismaccording to one aspect of the present invention;

FIG. 4 is a cross-sectional view of the energy storage mechanism in afirst position;

FIG. 5 is a cross-sectional view of the energy storage mechanism in asecond position;

FIG. 6 is a cross-sectional view of the energy storage mechanism in athird position;

FIG. 7 is a cross-sectional view of the energy storage mechanism in afourth position;

FIG. 8 is a cross-sectional view of the energy storage mechanism in afifth position;

FIG. 9 is a graph showing the force generated by the energy storagemechanism;

FIG. 10 is a partially fragmentary cross-sectional view of a portion ofa mechanism according to another aspect of the present invention;

FIG. 11 is a partially fragmentary cross-sectional view of the mechanismof FIG. 10 showing the cam in a rotated position;

FIG. 12 is an isometric view of an energy storage mechanism according toanother aspect of the present invention;

FIG. 13 is an isometric view of the mechanism of FIG. 12;

FIG. 14 is an isometric view of the mechanism of FIG. 12;

FIG. 15 is an isometric view of the mechanism of FIG. 12;

FIG. 16 is an exploded isometric view of an energy storage mechanismaccording to yet another aspect of the present invention;

FIG. 17 is an isometric view of the energy storage mechanism of FIG. 16wherein the mechanism is in an extended position;

FIG. 18 is an isometric view of the mechanism of FIG. 17 wherein themechanism is in a retracted position;

FIG. 19 is a partially schematic side elevational view of the mechanismof FIGS. 16-18 in a retracted position;

FIG. 20 is a partially schematic view of the mechanism of FIG. 18immediately prior to release of the cam;

FIG. 21 is a partially schematic side elevational view of the mechanismof FIG. 19 immediately after the cam rotates due to release of themechanism; and

FIG. 22 is a partially fragmentary side elevational view of a foldingseat and control mechanism according to another aspect of the presentinvention;

FIG. 23 is a partially fragmentary side elevational view of the foldingseat of FIG. 22, wherein the seat assembly is in a forward/foldedposition;

FIG. 24 is a partially fragmentary view of a control mechanism of theseat of FIGS. 22 and 23, wherein the control mechanism is in afirst/non-actuated position;

FIG. 25 is a partially fragmentary view of the control mechanism of FIG.24, wherein the control mechanism is in a second actuated state;

FIG. 26 is a partially fragmentary isometric view of the mechanism ofFIGS. 24 and 25;

FIG. 27 is a partially fragmentary enlarged view of a portion of theseat of FIG. 22;

FIG. 28 is an isometric view of the housing of the mechanism of FIGS.24-26; and

FIG. 29 is an isometric view of a stop of the mechanism of FIGS. 24-26.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENT

For purposes of description herein, the terms “upper,” “lower,” “right,”“left,” “rear,” “front,” “vertical,” “horizontal,” and derivativesthereof shall relate to the invention as oriented in FIG. 3. However, itis to be understood that the invention may assume various alternativeorientations and step sequences, except where expressly specified to thecontrary. It is also to be understood that the specific devices andprocesses illustrated in the attached drawings and described in thefollowing specification are simply exemplary embodiments of theinventive concepts defined in the appended claims. Hence, specificdimensions and other physical characteristics relating to theembodiments disclosed herein are not to be considered as limiting,unless the claims expressly state otherwise.

With reference to FIG. 1, an energy storage mechanism 1 according to oneaspect of the present invention may be mounted in a folding vehicle seatassembly 10. Mechanism 1 provides an axial force tending to move(rotate) the seat assembly 10 from the use position of FIG. 1 to thefolded position shown in FIG. 2, and also assists in moving the seat ina controlled manner from the folded configuration of FIG. 2 back to theuse position of FIG. 1. As described in more detail below, energystorage mechanism 1 is capable of generating a force that assists a userin folding and unfolding the seat assembly 10, without requiring the useof powered actuators or the like.

Seat assembly 10 includes a seat base structure 11 and a seat backstructure 12 that is pivotally mounted to the base structure 11 at apivot 13. The seat back 12 and cushion 14 can be pivoted about pivot 13from an upright position “U” to a lowered position “L”. A seat cushion21 is secured to the seat base structure 11. When the seat backstructure 12 is folded forward, the back cushion 14 may contact the seatcushion 21 as shown in dashed lines in FIG. 1, and in solid lines inFIG. 2. Pivot 13 includes a pivoting/latching mechanism (not shown) of aknown design that may be releasable to permit pivoting of the back 12and cushion 14 from the upright position U.

The seat base structure 11 is pivotably mounted to a fixed seat supportbracket/structure 15 at pivot 16. The folding vehicle seat assembly 10may include a torsion spring (not shown) of a known design acting aboutthe pivot 16 tending to shift the seat from the use configuration ofFIG. 1 to the folded configuration of FIG. 2. Prior folding seatsincluded a pair of such torsion springs as well as dampening devices tocontrol the rate of rotation of the seat as moving from position 1 toposition 2. However, the energy storage mechanism 1 permits eliminationof one or both of the torsion springs previously used at pivot 16 aswell as any dampeners used to control the rate of rotation of the seat,thereby reducing the complexity and attending cost of the folding seatassembly 10. The fixed structure 15 is securely connected to vehiclefloor structure 17. A releasable latch mechanism 18 securely yetreleasably interconnects a rear portion 19 of seat base structure 11 toa fixed latch component 20 fixed to vehicle floor structure 17 toselectively prevent rotation of seat base 11 about pivot 16. Thepivoting and latching mechanism 13 is connected to the latch mechanism18 by a known device such as a rigid link, Bowden cable, or othersuitable arrangement. As discussed in more detail below, the releasablelatch mechanism 13 is operably connected to mechanism 1 by a cableassembly 55, and actuation (release) of mechanism 1 causes mechanism 1to selectively release latch 13 to initiate the rotation of the back 12and cushion 13 from position U to position L. Upon completion of thisrotation the mechanism at pivot 13 then transmits the remaining energyfrom mechanism 1 to selectively release latch 18 to permit rotation ofseat base 11 from the use position (FIG. 1) to the folded configuration(FIG. 2). The releasable latch mechanisms 13 and 18 may be of a knowndesign, such that they will not be described in detail herein.

With further reference to FIG. 3, an energy storage mechanism 1according to one aspect of the present invention includes a housing 2having a first part 3 that is interconnected to a second part 4 duringassembly of the energy storage mechanism 1. A cam 5 is pivotally mountedin the housing 2 for rotation about a pivot 6. As described in moredetail below, a first movable spring engagement part 7 includes a camfollower portion 8 that slideably contacts cam outer surface 9 to shiftthe first movable spring engagement part 7 along axis “S” upon rotationof cam 5.

A coil spring 25 is mounted within a cylindrical portion 26 of housing2, and a first end 27 of coil spring 25 bears against an annular surface28 of first movable spring engagement part 7. Coil spring 25 is coiledabout a cylindrical portion 29 of first movable spring engagement part7. It will be understood that other resilient members and/or devicessuch as gas springs or the like could be utilized instead of coil spring25.

An elongated rod 30 is slideably received in a cylindrical bore 31 offirst movable spring engagement part 7 for movement along axis Srelative to first movable spring engagement part 7. A pin 33 is fixed tofirst movable spring engagement part 7, and extends transversely throughelongated slot 32 in elongated rod 30. Pin 33 thereby limits the travelof elongated rod 30 relative to first movable spring engagement part 7.When the rod 30 is in the fully extended position relative to the firstmovable spring engagement part 7 (FIG. 3), pin 33 is in contact with afirst end 34 of elongated slot 32 and prevents further extension ofelongated rod 30. As described in more detail below, in operation,elongated rod 30 may be pushed inwardly into bore 31 of first movablespring engagement part 7, and contact between pin 33 and second end 35of elongated slot 32 limits the travel of elongated rod 30 when it ispushed into bore 31 of first movable spring engagement part 7.Alternately, an annular flange or ridge 37 of rod 30 contacts end 38 oftubular portion 41 of a second movable spring part 40 to limit inwardtravel of rod 30 relative to part 40.

Second movable spring engagement part 40 includes elongated tubularportion 41 having a cylindrical bore 42 that slideably receiveselongated rod 30. Tubular portion 41 of second movable spring engagementpart 40 is slideably received in an aperture or opening 43 in an endpiece 44 that is mounted to housing 2. The second movable springengagement part 40 includes a disc-shaped end 45 disposed in acylindrical cavity portion 47 of housing 2 in contact with second end 48of coil spring 25. An annular flange 46 cups and locates end 48 of coilspring 25, and thereby ensures that the coil spring 25 bears againstdisc-shaped end 45 of second movable spring engagement part 40.

When the cam 5 of mechanism 1 is in the position illustrated in FIG. 3,the coil spring 25 bears against disc-shaped end 45 of second movablespring engagement part 40, thereby biasing the second movable springengagement part 40 into the position illustrated in FIG. 3. In thisposition, the disc-shaped end 45 of second movable spring engagementpart 40 bears against end piece 44, and end piece 44 acts as a stop thatlimits the outward travel of second movable spring engagement part 40relative to housing 2. End 36 of elongated rod 30 further includes anopening 39 forming a connector that can be utilized to connect theelongated rod 30 to fixed structure 15 at a pivot point 49 (FIG. 1).Housing 2 further includes a connector 50 that pivotably mountsmechanism 1 to seat base 11 at pivot 51 (FIG. 1).

A first Bowden cable assembly 55 operably connects first movable springengagement part 7 to latch mechanism 13. Cable assembly 55 includes aninner cable 56, and an outer tube or sheath 57. A fitting 59 secures endportion 60 of outer sheath 57 to the mechanism housing 2, and an endfitting 58 attached to inner cable 56 is secured to first movable springengagement part 7 at a connector 61. As described in more detail below,movement of first movable spring engagement part 7 shifts the innercable 56 of first Bowden cable assembly 55 to thereby selectivelyrelease the releasable latch mechanism 13.

A manual or electrical operating/release device such as lever 72 or thelike is operably connected to mechanism 1 by a second Bowden cableassembly 65. Cable assembly 65 includes an inner cable 66, and a sheath67. A first end fitting 68 is fixed to a first end 69 of inner cable 66.The end fitting 68 engages a stop surface 70 on cam 5 adjacent camsurface 9, and inner cable 66 passes through a slot 71 in cam 5 to forma lost motion mechanism. The slot 71 has a downwardly-opening U-shape incross section, such that, in operation, the end fitting 68 and innercable 66 can disengage completely from the cam 5 as cam 5 rotates to theposition shown in FIGS. 5 and 6. A second end 73 of inner cable 66 isconnected to a release mechanism such as a lever 72 or the like that canbe manipulated by a user to pull on inner cable 66.

With further reference to FIG. 4, in use, a cycle starts with themechanism 1 in the fully contracted position with elongated rod 30 fullyinserted into tubular portion 41 of second movable spring engagementpart 40. In this position, second movable spring engagement part 40 isshifted to the innermost position illustrated in FIG. 4, and cam 5 is inthe forwardly-rotated position illustrated in FIG. 4. In this position,spring 25 is fully compressed (relative to the other operating statesdescribed in more detail below). The configuration of FIG. 4 correspondsto the seat position illustrated in FIG. 1, wherein the seat basestructure 11 is in the lowered position, and latch mechanism 18 isengaged to secure the vehicle seat assembly 10 to the vehicle floorstructure 17.

To fold the seat assembly 10 from the position illustrated in FIG. 1 tothe position illustrated in FIG. 2, a user actuates release mechanism 72to shift inner cable 66 of second cable assembly 65 in the direction ofthe arrow “C1”. Movement of cable 66 causes end fitting 68 to pullagainst stop surface 70 of cam 5, thereby causing cam 5 to beginrotating about axis 6 in the direction of the arrow “R”. As the cam 5rotates, the cam surface 9 slides against cam follower surface 8 offirst movable spring engagement part 7, with spring 25 biasing camfollower surface 8 into engagement with cam surface 9. As the cam 5rotates in the direction of the arrow “R”, the end portion or lobe 75 ofcam 5 slides along cam follower surface 8 until the end portion 75travels beyond a line “L1” passing through the pivot axis 6 of cam 5.Once the end portion 75 travels beyond the point L1, the contact pointbetween cam follower surface 8 and cam surface 9 is offset below lineL1, such that the force of coil spring 25 acting on cam 5 creates amoment tending to rotate the cam 5 in the direction of the arrow “R”.The moment generated by coil spring 25 causes cam 5 to rotate as coilspring 25 expands until the cam 5 reaches the rearwardly-rotatedposition illustrated in FIG. 5. As discussed above, slot 71 in cam 5 hasan outwardly-opening U-shape in cross section. This permits the cableend 68 and cable 66 to disengage from cam 5 as shown in FIG. 5, suchthat the cam 5 can rotate in the direction of the arrow “R” under theforce of expanding coil spring 25 while inner cable 66 remainsstationary. Housing 2 preferably includes a retainer portion 76 thatretains the cable and fitting 66 in the position illustrated in FIG. 5after it is disengaged from the stop surface 70 of cam 5. A stop surface62 of housing 2 contacts side surface 63 of cam 5 to prevent rotation ofcam 5 beyond the position of FIG. 5. As first movable spring engagementpart 7 shifts relative to elongated rod 30, pin 33 of first movablespring engagement part 7 moves from second end 35 of slot 32 to acentral portion of slot 32 as shown in FIG. 5.

As the first movable spring engagement part 7 shifts from the positionillustrated in FIG. 4 to the position illustrated in FIG. 5, it pullsthe end fitting 58 of inner cable member 56, thereby releasing the latchmechanisms 13 and 18. Release of the latch mechanism 18, in turn,permits the seat base structure 11 to be rotated upwardly from theposition illustrated in FIG. 1 to the position illustrated in FIG. 2.

It will be appreciated that the mechanism 72 and cable 66 do not need tomove very far to cause the cam 5 to release and thereby cause the firstspring engagement part 7 to travel a relatively large distance as itmoves from the position illustrated in FIG. 4 to the positionillustrated in FIG. 5. Movement of first spring engagement part 7thereby provides a relatively large input movement to releasable latch18 via cable 55, even though the user may provide a relatively smallmovement at release device/lever 72. Also, the amount of force requiredto actuate device/lever 72 to rotate the cam 5 far enough to cause coilspring 25 to begin rotating the cam 5 is relatively low. Nevertheless,as the cam 5 rotates due to the force generated by coil spring 25, theforce acting on inner cable 56 and latch 18 is quite large.

With further reference to FIG. 9, as the mechanism shifts from theconfiguration of FIG. 4 (“circle A”) to the configuration of FIG. 5(“circle B”), the seat base 11 does not rotate. However, the amount offorce generated by the coil spring 25 drops significantly due to theexpansion of coil spring 25.

After the latch mechanism 18 is released, the mechanism 1 begins toassist upward rotation of seat base 11 by expanding length-wise as itshifts from the configuration illustrated in FIG. 5 to the configurationillustrated in FIG. 6. As the mechanism shifts from the configuration ofFIG. 5 to the configuration of FIG. 6, the second movable springengagement part 40 is shifted outwardly as coil spring 25 expands, andthe seat base 11 rotates upwardly. As second movable spring engagementmember 40 moves outwardly from the position of FIG. 5 to the position ofFIG. 6, end 38 of part 40 bears against annular ridge 37 of rod 30, andthereby pushes rod 30 outwardly. Movement of rod 30 relative to firstspring engagement part 7 causes pin 33 of part 7 to shift from a centralportion of elongated slot 32 as shown in FIG. 5 to the end 34 of slot 32shown in FIG. 6. With reference to FIG. 9, when the mechanism 1 is inthe configuration illustrated in FIG. 6 (“circle C”), the coil spring 25is fully extended, and the coil spring 25 does not generate forcetending to further rotate the seat base 11. At this point, the seat base11 is at a rotation angle of about fifty degrees relative to the useposition of zero degrees (FIG. 1). At about mid rotation, the center ofgravity 80 (FIGS. 1 and 2) of the moving portion (i.e., base 11 and back12) of the seat assembly passes over the pivot point 16, such that theseat base 11 and back 12 will tend to continue moving toward the foldedposition of FIG. 2 due to the moment generated due to the center ofgravity being forward of the pivot point 16. Also, as the seat base 11and back 12 are moved from the use configuration (FIG. 1) to the foldedconfiguration (FIG. 2), the momentum of the moving components will tendto cause the parts to continue moving even after mechanism 1 is notgenerating a force on seat base 11. As the center of gravity passes overthe pivot point 16, the momentum of the seat assembly will thereforetend to continue the rotation of the moving seat components. Thus, thecombined effects of the moment caused by the position of the center ofgravity and the momentum of the components tends to cause the seat torotate to the fully folded position of FIG. 2.

As the seat base 11 continues to rotate past fifty degrees relative tothe starting position, the mechanism 1 shifts from the configurationillustrated in FIG. 6 to the configuration illustrated in FIG. 7. Duringthis portion of the operation, the elongated rod 30 is pulled out of theelongated tubular portion 41 of second movable spring engagement part40, and the pin 33 pulls the first movable spring engagement part 7outwardly due to contact of pin 33 with the second end 35 of elongatedslot 32 in elongated rod 30. Movement of the first movable springengagement part 7 causes the cam follower surface 8 to move in thedirection of the arrow “S1” along axis S. A torsion spring (not shown)biases the cam 5 in a counterclockwise direction (i.e., opposite thearrow “R”) (FIG. 4). As the cam follower surface 8 moves in thedirection of the arrow “S”, the cam 5 rotates from the rearward positionshown in FIG. 6 to the forward position shown in FIG. 7. As the coilspring 25 is compressed, the force generated by the coil spring 25shifts from zero (“circle C”) (FIG. 9) to the “circle D” position ofFIG. 9.

As discussed above, the moving seat components 11 and 12 have storedenergy due to the momentum initially generated by expansion of coilspring 25 in moving from the configuration of FIG. 5 to theconfiguration of FIG. 6, and the seat also generates a moment aboutpivot 16 (FIG. 2) because the center of gravity 80 is forward of thepivot 16. The combination of the moment due to the center of gravity 80being forward of pivot 16, and the energy stored in the moving seatcomponents compress the coil spring 25 as the mechanism shifts from theconfiguration of FIG. 6 to the configuration of FIG. 7. In this way, themechanism 1 again stores some of the energy by compressing coil spring25 as the seat reaches the fully folded position illustrated in FIG. 2.It will be apparent that the energy stored by spring 25 as it iscompressed during the final portion of the movement to the position ofFIG. 2 acts as a cushion to slow the rotation of the seat componentsjust prior to reaching the folded configuration.

To shift the seat from the fully folded position illustrated in FIG. 2,wherein the mechanism 1 is in the configuration illustrated in FIG. 7, auser pulls on the seat to rotate it about the pivot axis 16. Initially,the mechanism 1 shifts from the configuration illustrated in FIG. 7 tothe configuration illustrated in FIG. 8 due to the elongated rod 30sliding into the cylindrical portion 41 of second movable springengagement part 40. During this movement, pin 33 slides from end 34 ofslot 32 (FIG. 7) to a central portion of slot 32 (FIG. 4). The forcerequired to slide elongated member 30 in tubular portion 41 of secondmovable spring engagement part 40 may be controlled to provide thedesired degree of resistance. For example, the force may be controlledby providing a tight or loose fit between the elongated rod 30 and theelongated portion 41 and by controlling the frictional coefficients ofthe materials used. Also, the force generated during motion of elongatedrod 30 relative to the cylindrical portion 41 may include a dampingcomponent. The damping component may be due to (for example) air movingbetween the elongated rod 30 and the cylindrical portion 41. Thus, theforce required to move elongated rod 30 relative to cylindrical portion41 of second movable spring engagement part 40 may include a frictionalcomponent that is an approximately constant force, and it may alsoinclude a component that is a linear (or non-linear) function ofvelocity to provide damping.

As the seat assembly moves from the configuration of FIG. 2 to theconfiguration of FIG. 1, the elongated rod 30 reaches the positionillustrated in FIG. 8, and the flange 37 of elongated rod 30 bearsagainst end 38 of cylindrical portion 41. The second movable springengagement part 40 then moves from the configuration illustrated in FIG.8 to the configuration in FIG. 4, thereby compressing coil spring 25. Asrod 30 moves relative to part 7, pin 33 moves from a central portion ofslot 32 (FIG. 8) of rod 30 to end 35 of slot 32 (FIG. 4). Once the seatassembly returns to the position illustrated in FIG. 1, the coil spring25 is fully compressed as illustrated in FIG. 4. At this point, a usercan repeat the cycle by releasing the cam 5 by manipulating releasemechanism 72 as described above.

With further reference to FIGS. 10 and 11, a mechanism 100 according toanother aspect of the present invention is similar to the energy storagemechanism 1 described above, except that the mechanism 100 includes anarrangement whereby one or more cables 101 are connected directly to acam 105, rather than to a component such as the first movable springengagement part 7 that moves with a cam follower. Cam 105 of mechanism100 includes a cam surface 106 that is cycloidal in shape. A camfollower 108 slideably engages the cam surface 106 to compress a spring(not shown) in substantially the same manner as the spring 25 discussedin detail above in connection with the mechanism 1. Although cam surface106 could have a variety of shapes, a cycloidal shape is presentlypreferred because the rate of change of the radius defined by the camsurface 106 is somewhat lower than the cam surface 9 of mechanism 1, andthe cam 105 therefore does not release as rapidly, such that the noiseand vibration upon actuation of the mechanism is reduced. Cam 105includes raised bosses 109, 110, 111 and 112. An end fitting 113connects cable 101 to boss 109, and an end fitting 114 interconnectscable 102 to boss 110. Similarly, a fitting 111 connects cable 103 toboss 111, and a fitting 116 connects cable 104 to boss 112.

An end 96 of a release cable 95 is operably interconnected to cam 105 bya lost motion mechanism that is substantially similar to the arrangementdescribed in detail above in connection with the mechanism 1 (FIG. 3).Housing 97 of mechanism 100 includes a wall portion 98 that separatesthe end portion and end fitting 96 of cable 95 from the cables 101-104.

In use, a user generates a force on cable 95 tending to rotate the cam105 in a clockwise direction from the position illustrated in FIG. 10.As the cam follower 108 passes over the end lobe surface 99 of cam 105,the force generated by the main spring (not shown) causes the camfollower 108 to rotate the cam 105 in a clockwise direction from theposition illustrated in FIG. 10 to the position illustrated in FIG. 11.As the cam 105 rotates, it pulls on the cables 101-104, therebyactuating a plurality of mechanisms. Also, cam 105 includes a hub 117,and one or more of the cables 101-104 wrap around the hub 117 as the cam105 rotates to the position illustrated in FIG. 11 to thereby ensurethat the cables 101-104 are pulled the desired distance. The raisedbosses 109-112 may be positioned at different heights along axis 118 ofcam 105 to ensure that the cables 101-104 pass over one another when thecam 105 rotates to the position illustrated in FIG. 11.

The mechanism 100 provides for four different outputs, such that themechanism 100 can actuate four separate latch mechanisms or the like. Inthe illustrated example, the cables 101 and 102 are each connected to amain latch 18 (FIG. 1), and the cable 103 is operably connected to alatch 13 to release the seat back 12 relative to the base 11. The cable104 is operably connected to a latch mechanism of a folding headrest(not shown). Such folding headrests and latch mechanisms are known, suchthat the details of the headrest and headrest mechanism are notdescribed in detail herein.

The position of the bosses 109-112 can be selected to provide thedesired amount of travel and force on the cables 101-104 as required toactuate the specific mechanism connected to each of the cables 101-104.Furthermore, the position of the bosses 109-112 also controls the timingof the actuation of the mechanisms connected to the cables 101-104. Inthe illustrated example, the cables 101 and 102 are both connected tolatch mechanisms 18 that secure the seat to the vehicle floor. Thecables 101 and 102 actuate the latch mechanisms 18 at virtually the sametime. The position of boss 112 is selected to cause cable 104 to actuatethe headrest latch mechanism (not shown) quickly, such that the headrestlatch is released before the latches 18. The boss 111 is positioned topull on cable 103 and actuate a latch mechanism at pivot 13 (FIG. 1)immediately after the headrest latch mechanism is actuated, but prior toactuation of the latches 18.

Although mechanism 100 is illustrated as including four bosses thatoperably connect four different cables to the mechanism 100, the numberof cables operably connected to the cam 105 may be varied for aparticular application as required to actuate the number of latchesutilized in a particular seat design.

With further reference to FIG. 12, a mechanism 120 according to anotheraspect of the present invention includes a housing 121 that pivotablysupports a cam 122 defining a cam surface 123 that slideably engages acam follower 124 that is connected to a coil spring 125. An input cable129 is operably connected to the cam 122, and rotates the cam 122 in thedirections of the arrow B when the input cable 129 is shifted in thedirection of the arrow A. In operation, input cable 129 is shifted inthe direction of the arrow A, and a “lost motion” interconnection formedby retainer 131 of cam 122 and ball end 130 of cable 129 initiallyrotates cam 122 through a few degrees of motion from the positionillustrated in FIG. 12 as a result of the force of ball end 130 actingon retainer 131 of cam 122. However, after the cam 122 rotates past afew degrees, the action of spring 125 and cam follower 124 on camsurface 123 generates a force on cam 122 causing the cam 122 to rotatein the direction of the arrow B without further movement of ball end130. As shown in FIG. 13, retainer 131 of cam 122 disconnects from ballend 130 after a few degrees of rotation thereby providing a lost motioninterconnection.

The input cable 129 may be actuated manually by a strap, lever, or othermanual input device that is positioned to be readily accessible to auser. Alternately, a powered actuator such as a solenoid, electricmotor, or the like may also be operably connected to the cable 129 toshift cable 129 and thereby actuate mechanism 120.

Significantly, input cable 129/ball end 130 may move a relatively shortdistance (e.g., 10 mm), and a relatively small amount of force (e.g.,15-50 Newtons) on cable 129 may be sufficient to cause the cam 122 toshift from the position illustrated in FIG. 12 to the positionillustrated in FIG. 13. However, as the spring 125 moves from thecompressed position shown in FIG. 12 to the extended position shown inFIG. 13, spring 125 causes output cable 134 to travel a distance in thedirection of the arrow C by an amount (e.g., 50 mm) that issubstantially greater than that of input cable 129, and also produce aforce (e.g., 600-1200 Newtons) that is substantially greater than theforce needed to move the input cable 129. Thus, the input forces and/ordistances utilized to control/actuate mechanism 120 or substantiallyless than the output forces and/or distances provided by mechanism 120.Also, the mechanism 120 can be designed to accommodate a wide range oftravel requirements and force requirements for the output cable 134without changing the design of mechanism 120.

With reference to FIG. 14, actuation of spring return cable 139 by aforce F compresses spring 125, and a torsion spring (not shown) causescam 122 to rotate in the direction of the arrow D as the spring 125 iscompressed. As the cam 122 approaches the start position, ball end 130of cable 129 engages retainer 131 of cam 122, and causes input cable 129to shift in the direction of the arrow E. Although mechanism 120 may beutilized in a wide range of applications in a wide range of mountingconfigurations, in one application the spring return cable 139 isgrounded to a stationary connector on a vehicle floor or seat frame, andoutput cable 134 is operably connected to a movable headrest, armrest,“fold flat” seat, or a “tumble” seat. Movement of the headrest, armrest,or seat compresses spring 125 as the seat or other component is moved toa folded position, causing the mechanism 120 to shift from the stateshown in FIG. 13 to the state shown in FIG. 14. Conversely, as the seator other component unfolds, the spring changes from the compressedconfiguration shown in FIG. 12 to the extended configuration shown inFIG. 13, and the output force generated by the mechanism 120 assists inunfolding the seat or other component. It will be understood that, ingeneral, the seat or other component need not move from a foldedcondition to an unfolded condition and vice versa, but may merely shiftbetween two different configurations.

With further reference to FIG. 16, an energy storage mechanism 150according to yet another aspect of the present invention includes ahousing 151, and a cam 152 having an opening 153 that receives a boss154 of housing 151 when cam 152 is installed in housing 151 to form apivot 212 (FIG. 21). As described in more detail below, a torsion spring155 rotatably biases the cam 152 in a counterclockwise direction (whenoriented as shown in FIGS. 19-21) relative to housing 151. A cover 156may be secured to housing 151 utilizing threaded fasteners 157. A camfollower assembly 158 includes an elongated body 159 and a followerwheel 160 that is rotatably mounted to the elongated body 159. Anelongated tube 165 includes an outer end 166 to which an end piece 167is mounted. When assembled, tube 165 is slideably received in elongatedportion 161 of housing 151, and elongated body 159 of cam followerassembly 158 is slideably received within tube 165 (see also FIGS. 17and 18). When assembled, a coil spring 170 contacts outer end 171 ofbody 159 of cam follower assembly 158, and also contacts end piece 167fixed to elongated tube 165. The coil spring 170 thereby biases the tube165 towards an extended position relative to the cam follower assembly158. An O-ring 172 fits around end 171 of elongated body 159 to securethe O-ring 172 to the elongated body 159. O-ring 172 provides anair-tight, slideable seal between the cam follower assembly 158 andinner surface 173 of tube 165. As described in more detail below, endpiece 167 includes a relatively small orifice 214 that controls the flowof air into tube 165 in the region between the end 171 of body 159 andouter end 166 of tube 165. This restriction of air flow limits the rateat which tube 165 will extend relative to cam follower assembly 158 dueto the force of coil spring 170.

With further reference to FIGS. 17 and 18, wheel 160 of cam followerassembly 158 rotatably engages cam surface 178 of cam 152. A firstrelease cable 176 includes an end fitting 177 that is received in anarcuate slot 178 of cam 152. Similarly, a second release cable 179includes an end fitting 180 that is received in an arcuate slot 181 ofcam 152. As described in more detail below, the release cables 176 and179 may be pulled either manually by a release lever 200 or by anelectrically powered actuator 201 to rotate cam 152 in a clockwisedirection (FIG. 17) to thereby release the mechanism 150.

An interlock cable 185 includes an end fitting 186 that is received inarcuate slot 178 of cam 152. If end fitting 186 engages end 187 ofarcuate slot 178, the cable 185 prevents rotation of cam 152 in aclockwise manner that would otherwise occur if a tension force isapplied to one or both of the release cables 176 and 179. Interlockcable 185 may be operably connected to the seat back 12 (FIG. 1), suchthat cable 185 prevents rotation of cam 152 unless the seat back 12 isin the lower position “L”. Alternately, the cable 185 may be configuredto prevent rotation of cam 152 unless the seat back 12 is sufficientlyclose to the lower position “L”. For example, cable 185 may be operablyconnected to the seat back 12, such that rotation of cam 152 isprevented unless the seat back 12 is within, for example, thirty degreesor forty-five degrees of the lowermost position “L”. As described inmore detail below, the interlock cable 185 thereby provides a safetyfeature to prevent movement of the seat about pivot 16 (FIG. 1) unlessthe seat back 12 is in the lowermost position “L”. Thus, if an object ispositioned on the seat 21 such that seat back 12 cannot go to thelowermost position “L”, interlock cable 185 prevents release ofmechanism 150, and thereby prevents release of release latch mechanism18.

A plurality of output cables 190, 191, 192, and 193 are connected to thecam 152 at connection points 194, 195, 196, and 197, respectively. Asalso described in more detail below, rotation of cam 152 in theclockwise direction (FIG. 17) shifts (i.e., pulls) the output cables190-193 to thereby generate output forces. In the illustrated example,cables 191 and 193 comprise “first stage” cables that move a relativelylarge distance during the initial rotation of cam 152 from a restposition (FIG. 19) to an intermediate position (FIG. 20). The cables 190and 192 comprise “second stage” cables that do not move significantly asthe cam rotates from the position illustrated in FIG. 19 to the positionshown in FIG. 20, but do, however, move significantly as the cam 152moves from the position shown in FIG. 20 to the position shown in FIG.21. In the illustrated example, the first stage cables 191 and 193 areutilized to release a conventional pawl and ratchet mechanism 183 (FIGS.1 and 2) that locks the seat back 12 at a desired angular position aboutpivot 13 (FIG. 1). The second stage cables 190 and 192 operate torelease latch mechanism 18. In general, seat back 12 may include a pairof pawl and ratchet mechanisms, and each first stage cable 191 and 193connects to one of the pawl and ratchet mechanisms. Similarly, a pair oflatch mechanisms 18 may be utilized to latch the seat base structure tothe vehicle floor 17, and each second stage output cable 190 and 192connects to one of the latch mechanism 18.

It will be understood that the location of the connection points 194-197on cam 152 control the amount of movement of the output cables 190-193due to rotation of cam 152. Specifically, connection points 194 and 197are chosen to provide for a relatively large amount of motion of firststage cables 191 and 193 during the rotation of cam 152 from the “rest”position of FIG. 19 to the position of FIG. 20, yet provide relativelylittle motion of first stage cables 191 and 193 as cam 152 furtherrotates from the position of FIG. 20 to the position of FIG. 21.Conversely, the connection points 194 and 196 for second stage outputcables 190 and 192, respectively, are selected to provide for relativelysmall movement of cables 190 and 192 as cam 152 moves from the positionof FIG. 19 to the position of FIG. 20, while providing for a relativelylarge amount of movement of second stage output cables 190 and 192 ascam 152 further rotates from the position of FIG. 20 to the position ofFIG. 21.

With further reference to FIG. 19, mechanism 150 is in a “rest” orretracted position when the vehicle seat assembly 10 is in the useposition illustrated in FIG. 1. Input or release cable 176 may beoperably connected to a release lever or latch 200 that can be manuallyoperated by a user to generate a tension on cable 176. Cable 179 may beconnected to an electrical actuator 201 that can be actuated by a userto generate a tension on cable 179. In general, manual release lever 200provides a back up to permit release of mechanism 150 in the eventelectrical actuator 201 fails. It will be understood that device 150 mayutilize only the manual release lever 200 or it may utilize only theelectrical actuator 201. As discussed above, end fitting 186 ofinterlock cable 185 engages arcuate slot 178 in cam 152. Interlock cable185 may be operably connected to the seat back 12 (FIG. 1), such thatfitting 186 prevents rotation of cam 152 beyond the position illustratedin FIG. 20 unless the seat back 12 is in the lowered position “L” (FIG.1), or in the event the seat back 12 is not sufficiently close to thelowermost position “L”. In the illustrated example, the fitting 186 andinterlock cable 185 are configured to permit rotation of the cam 152from the position illustrated in FIG. 19 to the position illustrated inFIG. 20 even if the seat back 12 is not in the lowermost position “L”,yet prevent rotation of cam 152 from the position illustrated in FIG. 20to the position illustrated in FIG. 21 unless seat back 12 is in thelowermost position “L”, or sufficiently close thereto. When cam 152 isin the position illustrated in FIG. 19, first stage output cables 191and 193 prevent release of the pawl and ratchet mechanisms (not shown)that control rotation of seat back 12 about pivot 13. Also, when cam 152is in the position illustrated in FIG. 19 (or a position between that ofFIGS. 19 and 20), the second stage output cables 190 and 192 do notrelease the latch mechanisms 18, such that the seat assembly 10 cannotpivot about pivot 16.

As lever 200 is moved through an initial range of movement, cable 176rotates cam 152 from the position illustrated in FIG. 19 to the positionillustrated in FIG. 20, provided interlock cable 185 is configured topermit rotation of cam 152 in this manner. In the illustrated example,end fitting 186 of cable 185 is spaced apart from the end of slot 178when cam 152 is in the rest position (FIG. 19). Thus, cable 185 does notrestrict movement of cam 152 from the position of FIG. 19 to theposition of FIG. 20. Powered actuator 201 may be configured to providefor an initial movement of input cable 179 to rotate cam 152 from theposition illustrated in FIG. 19 to the position illustrated in FIG. 20.The portion 205 of cam surface 175 between groove 206 and cam lobe peak207 has a radius that increases slightly, such that wheel 161 of camfollower assembly 158 shifts the cam follower assembly 158 slightly ascam 152 rotates from the position shown in FIG. 19 to the position shownin FIG. 20 to thereby compress coil spring 170 slightly. The forcegenerated by coil spring 170 thereby biases the cam 152 from theposition shown in FIG. 20 back to the rest position shown in FIG. 19.Torsion spring 155 is configured to bias cam 152 towards the positionillustrated in FIG. 19. Thus, if torsion spring 155 is large enough, camsurface portion 205 may have a constant radius, and torsion spring 155may provide the sole rotational force biasing cam 152 to the positionillustrated in FIG. 19. In use, a user may actuate lever 200 or poweredactuator 201 to cause the cam 152 to rotate from the position shown inFIG. 19 to the position shown in FIG. 20. If the user then releases thelever 200 or powered actuator 201, cam 152 will initially rotate fromthe position shown in FIG. 20 back to the position shown in FIG. 19 dueto the bias of torsion spring 155 and/or the bias generated by spring170 due to wheel 160 contacting cam surface portion 205. In this way, aninitial motion of lever 200 or powered actuator 201 can be utilized torelease the pawl and ratchet adjustment mechanism 183 (FIGS. 1 and 2)due to motion of first stage cables 191 and 193 to permit rotation ofseat back 12 about pivot 13 without releasing latches 18.

If the manual release lever 200 or electrical actuator 201 are furtheractuated to further move cable 176 and/or cable 179 and thereby rotatecam 152 beyond the position illustrated in FIG. 20 towards the positionof FIG. 21, the wheel 160 of cam follower 158 will pass over the camlobe peak 207. As cam 152 continues to rotate, wheel 160 will travelalong cam surface portion 209. The contour of cam surface portion 209and the line of action of cam follower assembly 158 relative to pivot212 is configured such that spring 170 generates a relatively largerotational force tending to rotate cam 152 from the position of FIG. 20to the position of FIG. 21. Once follower wheel 160 moves past cam lobepeak 207, spring 170 expands, and the force generated by spring 170causes cam 152 to rotate from the position shown in FIG. 20 to theposition shown in FIG. 21. The rotational force generated by spring 170on cam 152 when follower wheel engages cam surface portion 209 issubstantially greater than the biasing force generated by torsion spring155, such that cam 152 generates a relatively large force pulling on“second stage” cables 190 and 192 to ensure that cables 190 and 192release latches 18 and permit upward rotation of the seat assembly. Ascam 152 rotates from the position shown in FIG. 20 to the position shownin FIG. 21, the second stage output cables 190 and 192 movesignificantly, releasing the latch mechanisms 18 to thereby permitmovement of the seat assembly from the position shown in FIG. 1 to theposition shown in FIG. 2. Cam lobe peak 207 may include a smallprotrusion or detent 208. Detent 208 provides tactile feedback to a usermanipulating lever 200, and helps to ensure that cam 154 is notinadvertently rotated beyond the position shown in FIG. 20 if a useronly desires to release the pawl and ratchet mechanisms 183 to permitangular adjustment of seat back 12 about pivot 13. It will be understoodthat mechanisms 183 may include a torsion spring that biases seat back12 about pivot 13.

As the cam 152 rotates from the position shown in FIG. 20 to theposition of FIG. 21, spring 170 begins to expand, thereby shifting tube165 outwardly with respect to the other portions of the mechanism 150.Fitting 167 of tube 165 is pivotally connected to fixed structure 15(FIG. 1) at 39, such that extension of tube 165 relative to the otherportions of mechanism 150 is prevented if latches 18 are engaged.However, once the second stage cables 190 and 192 release latches 18,the seat assembly 10 is free to rotate from the position shown in FIG. 1to the position shown in FIG. 2, and spring 170 continues to expandafter cam 152 rotates to the position of FIG. 21, thereby assisting inmovement of the seat assembly to the upright position shown in FIG. 2.It will be understood that FIG. 21 shows cam 152 immediately after itrotates to release latches 18, but before spring 170 has fully expandedto extend tube 165 and rotate the seat assembly from the position ofFIG. 1 to the position of FIG. 2.

A small orifice 214 through end piece 167 fluidly connects cavity 215formed by tube 165 and end 171 of body 159 of cam follower 158 due tothe sealing action of O-ring 172 on the inner side wall of tube 165. Asspring 170 expands and tube 165 extends away from cam follower assembly158, the volume of the cavity 215 increases. The size of the orifice 214through end piece 167 is selected to restrict air flow into the cavity215, thereby providing a damping force that limits the rate at whichtube 165 extends due to the forces generated by spring 170.

Referring again to FIGS. 1 and 2, as the seat assembly 10 rotates fromthe position shown in FIG. 1 to the position shown in FIG. 2, the centerof gravity 80 moves over the pivot point 16, such that the weight of theseat assembly 10 assists rotation after center of gravity 80 passes overpivot 16. Also, as the energy stored in coil spring 170 is expended, theseat assembly 10 gains momentum tending to continue rotation of the seatassembly 10 from the position shown in FIG. 1 to the position shown inFIG. 2. As the seat assembly 10 approaches the fully folded positionshown in FIG. 2, it generates a tension force tending to pull tube 165away from the other portions of mechanism 150. This force pulls thespring 170 away from cam follower assembly 158, such that wheel 160 ofcam follower assembly 158 is no longer biased into contact with cam 154by spring 170. At this point, the torsion spring 155 causes the cam torotate from the position shown in FIG. 21 back to the position shown inFIG. 19 to thereby reset the cam 152. The seat assembly may include oneor more torsion springs 188 biasing the seat towards the folded positionof FIG. 2. Torsion springs 188 may be utilized to assist the energystorage mechanism, and thereby reduce the size of coil spring 170.

If a user desires to move the seat assembly 10 from the upright positionshown in FIG. 2 back to the use position shown in FIG. 1, a usermanually applies a force on the seat assembly 10 causing the seatassembly 10 to rotate back to the position shown in FIG. 1. As the seatassembly 10 is rotated to the use position, the tube 165 is pushedinwardly until it returns to the fully retracted position illustrated inFIG. 19. Once the seat assembly 10 is fully rotated to the use positionshown in FIG. 1, the latches 18 are engaged to thereby retain the seatassembly 10 in the use position shown in FIG. 1.

Energy storage mechanism 150 may be configured to generate forces duringoperation as shown in FIG. 9 and described in more detail above inconnection with mechanism 1.

With further reference to FIGS. 22 and 23, a folding and sliding seatassembly 220 according to another aspect of the present invention thatincludes a control mechanism 240 that can be actuated to permit movementof the seat assembly 220 from the upright/use position of FIG. 22 to thefolded/forward position of FIG. 23. Seat assembly 220 includes a supportstructure 221 that may be rigidly secured to a vehicle floor structure222 or the like. The seat assembly 220 also includes a seat basestructure 223 and a seat back structure 224 that is pivotably mounted tothe seat base 223 by a pivot connection 225. The seat base is slideablymounted to the support structure 221 by linear slides 226 for movementbetween rearward position (FIG. 22) and a forward position (FIG. 23). Abiasing mechanism such as a spring or springs 227 bias the seat base 223towards the forward position of FIG. 23. In the illustrated example, thelinear slides 226 are positioned at a non-zero angle θ relative to thevehicle floor 222. Although the angle θ could be 0 degrees such that theseat back 224 translates horizontally, the angle θ is preferably in arange of about 5 degrees to 15 degrees. Alternately, the angle θ couldbe negative in some cases. Various support structures, seat basestructures, linear slides, springs and/or other biasing mechanisms areknown in the art, such that the details of these features will not bedescribed in detail herein.

A torsion spring 228 interconnects the seat back 224 and seat base 223,and biases the seat back 224 towards the folded position (FIG. 23) fromthe upright position (FIG. 22). The seat assembly 220 may include a pairof pivot structures 225 and a pair of torsion springs 228 with one ofeach being positioned on each side of the seat structure. Various pivotstructure(s) 225 and torsion spring(s) 228 are known in the art, suchthat these features will not be described in detail herein.

Control mechanism 240 is operably connected to first and second latches230 and 232, respectively, and mechanism 240 selectively releaseslatches 230 and 232 to permit sliding and pivoting of the seat assembly220 from the use position of FIG. 22 to the folded position of FIG. 23.

First releasable latch 230 is configured to selectively retain the seatback 224 in the upright position of FIG. 22, or permit rotation of seatback 224 relative to seat base 223 to the folded position of FIG. 23upon release of first latch 230. Seat assembly 220 may include a pair offirst latches 230 at each side of the seat assembly 220. The first latch230 may be of a known design, such that the first latch 230 will not bedescribed in detail herein. Second latch 232 (FIG. 22) selectivelyretains the seat base 223 in the rearward position of FIG. 22 relativeto the support structure 221, and permits movement of the seat base 223towards the forward position of FIG. 23 upon release of the second latch232. In the illustrated example, the second latch includes a hook-likefirst part 233 that is movably mounted on the seat base 223, and asecond part 234 as mounted on the support structure 221. It will beunderstood that second latch 232 could have different configurationsdepending upon the requirements of a particular seat design. Variouslatches for selectively retaining a vehicle seat in a fore-aft positionare known in the art, and the latch 232 will therefore not be describedin detail herein.

The first latch 230 is operably connected to a control mechanism 240 bya connector such as first cable 242, and second latch 232 is operablyconnected to control mechanism 240 by a connector such as second cable244. As described in more detail below, control mechanism 240 isoperably interconnected to the seat back 224 by a reset cable 246 thatresets mechanism 240 upon movement of the seat from the foldedconfiguration (FIG. 23) to the use position (FIG. 22). Control mechanism240 is also operably connected to an input device 250 by an input orrelease cable 248. Input cable 248 may comprise a Bowden-type cable, andinput device 250 may comprise a lever or the like. Alternately, inputdevice 250 may comprise an electrical switch, input/release cable 248may comprise an electrical line or the like, and an electric motor orother powered actuator (not shown) could be mounted on or adjacentcontrol mechanism 240 to provide for actuation of control mechanism 240.In the illustrated example, the control mechanism 240 is mounted to theseat base structure 223. However, the control mechanism 240 could bemounted to the support structure 221, vehicle floor 222, seat back 224,or other locations, depending upon the requirements of a particularapplication.

With further reference to FIGS. 24-26, control mechanism 240 includes ahousing 255 and a pinion member 256 that is rotatably mounted in thehousing 255 for rotation about a pin or rod 257 defining an axis ofrotation “A”. Pinion 256 includes a plurality of gears 258 arranged inan arc of a circle that engage linear gears 259 of rack member 260. Rackmember 260 is slideably disposed in a space 261 defined by side walls262 and 263 of housing 255 (see also FIG. 28), such that rack member 260moves in a linear reciprocating manner in the direction of the arrow“B”. A lock member 265 is slideably mounted within housing 255 forreciprocating motion in the direction of the arrow “C”. A coil spring266 provides a biasing force acting on rack member 260, thereby urgingrack member 260 to move in the direction of the arrow “B”. However, whenthe lock member 265 is in its extended position shown in FIG. 24, lockmember 265 prevents movement of rack member 260 from the retractedposition “R” shown in FIG. 24. As discussed in more detail below, lockmember 265 may be shifted to a retracted position (FIG. 25), therebyallowing rack member 260 to move to its extended position “E” shown inFIG. 25 due to the forces generated by spring 266.

Referring again to FIG. 24, pinion member 256 includes an arm 267 thatextends outwardly away from the pivot axis “A”. A first output cable 270includes a first end 271 that is connected to a connection point 268 onarm 267 of pinion member 256. A second end 272 of first outlet cable 270is connected to a splitter block 273 that is slideably disposed in acavity 274 of housing 255 for reciprocating motion in the direction ofthe arrow “D”, (and opposite the arrow “D”). The splitter block 273 isconnected to first ends 278 and 279 of first and second cables 242 and244, respectively. Cables 242 and 244 may comprise Bowden cables havingouter sheaths 280 and 281, respectively, and inner cables 282 and 283,respectively. As discussed in more detail below in connection with FIG.27, and end fitting 309 (see also FIG. 26) may be utilized to connectcable 246 to seat back 224. Fittings 284 and 285 may be utilized toconnect the cables 242 and 244 to the housing 255, and connectors 243and 245, respectively (FIG. 26) may be utilized to connect cables 242and 244 to latches 230 and 232. A central portion 287 of first outputcable 270 extends along a curved guide wall 286 of housing 255 (see alsoFIG. 28) to thereby retain the central portion 287 of cable 270 inalignment opening 288 in a sidewall 289 of housing 255.

Reset cable 246 (FIG. 24) includes an inner cable 291 and an outersheath 290. The inner cable 291 is connected to rack member 260, suchthat a sufficiently large tension force “F1” on inner cable 291 willmove the rack member 260 from the extended position (FIG. 25) back tothe retracted position of FIG. 24. It will be understood that the force“F1” must be great enough to overcome the biasing force generated bycoil spring 266 if it is to move the rack member 260 in this manner. Asdiscussed in more detail below in connection with FIG. 27, an endfitting 309 (see also FIG. 26) may be utilized to connect cable 246 toseat back 224.

Input/release cable 248 includes an end 295 that is received in a slot296 of lock member 265 (see also FIG. 29) such that a tension force F2on cable 248 will tend to move lock member 265 in the direction of thearrow F2. A coil spring 294 is connected to a hook/retainer 325 on lockmember 265 (see also FIG. 29) and to a hook/retainer 326 on housing 255(see also FIG. 28). Spring 294 thereby interconnects the lock member 265with housing 255 and biases lock member 265 in the direction of thearrow “C” from the retracted position shown in FIG. 25 towards theextended or locked position shown in FIG. 24. As discussed in moredetail below, a powered actuator 307 may be operably connected to lockmember 265 by a cable 302. Powered actuator 307 may be utilized insteadof a manual release button or lever device 250, or it may be utilizedalong with a manual release mechanism.

A push button 297 may also be connected to lock member 265 to providefor release of mechanism 240. Push button 297 may be utilized in placeof manual device 250 and powered actuator 307, or it may be utilized inconjunction with one or both devices 250 and 307.

In use, when the seat assembly 220 is in the upright or use positionshown in FIG. 22, the control mechanism 240 will initially be in theconfiguration shown in FIG. 24 wherein the pinion member 256 and rackmember 260 are retained in their retracted/non-actuated positionswherein lock member 265 prevents movement of rack member 260. Tofold/slide the seat assembly 220 from the configuration of FIG. 22 tothe configuration of FIG. 23, a user first actuates powered actuator 307or moves input device 250, thereby generating a tension force “F2” oninput cable 248. Alternately, a user can push on button 297 to move lockmember 265 if control mechanism 240 is configured to include push button297. After the lock member 265 has been shifted to theretracted/actuated position of FIG. 25, force generated by spring 266causes rack member 260 to shift from the retracted position of FIG. 24to the extended position of FIG. 25. As the rack member 260 shiftslinearly in a direction opposite the arrow “B”, the rack member 260causes pinion member 256 to rotate in a counter clockwise direction dueto the engagement of gears 258 of pinion member 256 with gears 259 ofrack member 260. As pinion member 256 rotates from the position of FIG.24 to the position of FIG. 25, the pinion member 256 pulls on firstoutput cable 270, thereby shifting the splitter block 273 from theposition shown in FIG. 24 to the position shown in FIG. 25. Due to theposition of the connection point 268, pinion member 256 initially causesfirst output cable 270 to move a relatively large amount as pinionmember 256 rotates. However, as the pinion member 256 approaches theposition shown in FIG. 25, the movement of cable 270 as a function ofthe angular displacement of pinion member 256 is reduced. The lineardisplacement of cable 270 and splitter block 273 is a sine function ofthe angular displacement of pinion member 256. Although the displacementof output cable 270 as a function of the angular displacement of pinionmember 256 is reduced as the pinion member 256 moves from the positionof FIG. 24 to the position of FIG. 25, the force acting on cable 270 mayincrease as the pinion member 256 moves from the position of FIG. 24 tothe position of FIG. 25 as the length of a effective moment arm “M” isreduced. The effective moment arm “M” is shown as a line that isperpendicular to a straight end portion (line “L”) of the cable 270adjacent end 271 of cable 270 that passes through axis A of pinionmember 256. It would be understood that the actual force acting onoutput cable 270 is a function of the angular position of pinion member256 and the location of connection point 268, as well as the forces vs.deflection characteristics of coil spring 266. In general, because theforce generated by coil spring 266 is not perfectively linear, theforces generated on cable 270 as function of the angular displacement ofpinion member 256 are not an exact sine function. Furthermore, the shapeand location of curved guide wall 286 of housing 255 and location ofopening 288 may also effect the position of the line L and length ofeffective moment arm M. In a preferred embodiment, the force vs.deflection characteristics of spring 266 and the position of connectionpoint 268 are selected such that the forces on output cable 270 (andcables 242 and 244) are substantially constant s pinion member 256rotates. The connection location 268 and spring 266 can be selected toprovide a force and displacement of output cable 270 that meets therequirements of a particular application. In general, connectionlocation 268 and spring 266 can be configured such that the force oncable 270 is substantially constant, or it increases or decreases aspinion member 268 rotates.

With reference to FIG. 29, lock member 265 may include an extension 298that interconnects with push button 297. In the illustrated example, theextension 298 includes a flexible barbed connector 299 and an opening200 that receives an extension 301 of push button 297 to therebysnap-attach button 297 to extension 298 of lock member 265. Push button297 may be used instead of mechanism 250 or powered actuator 307.Alternately, push button 297 may be utilized in addition to mechanism250 and/or powered actuator 307 to provide for manual release of lockmember 265 in the event the mechanism 250 or powered actuator 307 isunable to generate sufficient force to move the lock member 265 from theengaged position of FIG. 24 to the retracted position of FIG. 25.Specifically, a user can push on button 297 to shift the lock member 265to the release position of FIG. 25 if necessary.

In addition to the input cable 248 that is connected to the input device250, the control mechanism 240 may also include a second input cable 302that is also operably interconnected with the lock member 265. The inputcable 248 may extend through an opening 303 (see also FIG. 28) inhousing 255, and cable 302 may extend through opening 304 in housing255. End 305 of input cable 302 is received in slot 296 of lock member265. End 306 of input cable 302 may be connected to powered actuator307. The powered actuator 307 may comprise an electrically-poweredlinear actuator that is operably connected to an electrical power supplysystem of the vehicle (not shown). A switch 327 may be positioned on anactuator 307, or it may be positioned at a remote location such as avehicle dashboard, interior door panel, or the like.

As discussed above, output cable 270 may be operably connected to afirst and second cables 242 and 244 by a splitter block 273 (FIGS. 24and 25). Alternately, a single output cable 270 may be utilized if twooutput cables are not required for a particular application. Thus,although a cable 270 is illustrated as being installed along with cables242 and 244 in FIG. 26, it will be understood that this is forillustration purposes, and if a single cable 270 is utilized to actuateone or more latches, the single cable 270 would be utilized in place ofthe cables 242 and 244.

With reference to FIG. 27, end 308 of reset cable 246 includes an endfitting 309. An extension 310 of seat back 224 extends downwardly awayfrom the pivot connection 225 about which seat back 224 rotates relativeto seat base 223. Outer sheath 313 of cable 246 is connected to seatbase 223 by a bracket 314, and inner cable 315 of reset cable 246 isslideably received in an opening 312 of a boss 311 of extension 310 ofseat back 224. As the seat back 224 rotates to the folded position “F”,fitting 309 at end 308 of inner cable 315 contacts boss 311, and themotion of the seat back 224 thereby generates a pull “F1” on the innercable 315. This force causes the rack member 260 to be shifted from theactuated/extended position of FIG. 25 to the retracted position of FIG.24. In the example illustrated in FIG. 27, the end fitting 309 isspaced-apart from boss 311 somewhat when seat back 224 is in the uprightposition to thereby create a “lost motion” effect whereby the seat back224 rotates through an initial range of motion before fitting 309contacts boss 311 and begins pulling on inner cable 315. The lost motioninterconnection is optional, however, and it may not be utilized if itis not required for a particular seat design. A stop 316 on seat base223 contacts extension 310 of seat back 224 upon rotation of seat back224 to the upright position to prevent rotation of seat back 224 beyondthe upright position. It will be understood that the reset cable 246 maybe operably interconnected with seat back 224 in a variety of differentways, depending upon the specific configuration of the seat base 223 andseat back 224. In a typical situation, the outer sheath 313 of cable 246is secured to seat base 223 utilizing a bracket 314 or the like, and end308 of inner cable 315 is inner connected to the seat back 224 at apoint that moves away from bracket 314 as seat back 224 rotates from itsupright position to its folded position.

With reference to FIG. 28, a cover 317 may be secured to the housing 255utilizing a plurality of threaded fasteners 318 that are received inopenings 319 of housing 255. Also, as discussed above, a central portion287 of cable 270 extends through opening 288 in housing 255, and thecable 270 slideably engages a curved guide wall 286 of housing 255.Housing 255 may also include a straight guide wall 320 that isspaced-apart from curved guide wall 286. The central portion 287 ofcable 270 is thereby received and guided between curved guide wall 286and straight guide wall 320. Housing 255 also includes a curved pinionsupport wall 321 that slideably engages an inwardly-facing cylindricalwall surface 322 (FIG. 25) of pinion member 256. A curved wall portion323 of housing 255 (see also FIG. 24) is configured to guide and retainpinion member 256 by sliding contact with gears 258 of pinion 256. Withfurther reference to FIG. 29, lock member 265 may include a channel 324that receives spring 294 to thereby bias lock member 265 into theextended position. Spring 294 connects to a hook or retainer 325 on lockmember 265, and to a hook or retainer 326 (see also FIG. 28) on housing255. Housing 255, pinion member 256, rack member 260, lock member 265and cover 317 may be made of polymer or other suitable materials.

As discussed above, the connection point 268 (FIGS. 24 and 25) on arm267 of pinion member 256 may be selected to provide a required force onthe output cables 242 and 244 as a function of the angular position ordisplacement of the pinion member 256. In a preferred arrangement, theforce generated by spring 266 on rack member 260 is reduced as thespring 266 approaches its extended position of FIG. 25. However, becausethe length of moment arm “M” becomes smaller as pinion member 256approaches the position of FIG. 25, the force on cables 242 and 244 isrelatively constant as the mechanism 240 moves from the configuration ofFIG. 24 to the configuration of FIG. 25. Cables 242 and 244 may also beconnected to pinion member 256 at different connection points to providefor different motions and forces for cables 242 and 244 as required fora particular application. Still further, additional output cables may bedirectly connected to the pinion member if additional latches or othermechanisms are to be actuated by the mechanism 240. For example, variousconnection points could be utilized for four different cables insubstantially the same manner as described in more detail above inconnection with the mechanism 150 of FIGS. 17-21. Also, the cables couldbe connected to the pinion member 256 utilizing slots to provide for alost motion-type operation if required to provide for a specific timingfor a particular application. Examples of such lost motion connectionsare described in more detail above in connection with the mechanism 150of FIGS. 17-21. For example, if a particular seat assembly requires thatlatch 230 is released before latch 232, first cable 242 could beconnected directly to pinion member 256, and cable 244 could beconnected to pinion member 256 utilizing a slot or other such lostmotion device to delay tensioning of cable 244 and release of latch 232.

The weight of the seat back 224 (FIG. 23) creates a moment about thepivot connection 225 as the seat back 224 moves toward the foldedposition of FIG. 23. The torsion spring (or springs) 228 also generatesa bias force tending to rotate the seat back 224 to the folded position.Mechanism 240 is designed such that these forces are sufficiently largeto overcome the forces generated by coil spring 266 (FIGS. 24 and 25) ofmechanism 240 as the seat back 224 moves from the upright position tothe folded position. In this way, the energy from torsion spring 228 andseat back 224 generated as the seat back 224 moves from the uprightposition to the folded position is stored in the coil spring 266 ofmechanism 240. This stored energy is later used to actuate the latches230 and 232 upon release of mechanism 240. In this way, a relativelysmall user input force on device 250 can be utilized to actuate themechanism 240, yet a relatively large output force on cables 242 and 244is generated to provide for release of latches 230 and 232. Alternately,a relatively low power/small electrically-powered actuator 307 may beutilized to release the mechanism 240. In contrast, existing latchrelease mechanisms typically do not store significant amounts of energyinternally, such that a relatively large manually-operated lever or thelike typically needs to be provided to enable a user to generatesufficient force to release the latches 230 and 232. Alternately,existing mechanisms that do not store energy may require use of arelatively large powered actuator capable of generating the relativelylarge forces required to directly release latches 230 and 232.

In the illustrated example, a linear coil spring 266 acts on rack member260 to thereby rotate pinion member 256. However, it will be understoodthat a torsion spring (not shown) acting directly on pinion member 256may be utilized instead of the rack 260 and coil spring 266. If atorsion spring is utilized in place of rack member 260 and coil spring266, lock member 265 is configured to act directly on pinion member 256to selectively retain the pinion member 256 in its retracted position.In general, if a relatively large output force acting on cables 242 and244 is required, a torsion spring acting on pinion member 256 may bepreferable. However, if a somewhat lower force on cables 242 and 244 isrequired, a coil spring 266 and rack member 260 may be preferable due tothe lower costs involved.

Mechanism 240 is shown in FIGS. 22 and 23 in connection with a slidingand folding vehicle seat. However, it will be understood that mechanism240 may be utilized in a variety of other applications. For example, themechanism could have a single output cable that releases a seat back fortilting, for fore-aft adjustment, or for height adjustment. Alternately,mechanism 240 may include numerous output cables that are operablyconnected to numerous latches or other devices.

The energy storage mechanism of the present invention permits a foldingseat to be operated by manipulation of a single release mechanism,lever, or the like. Also, as described above, the mechanism of thepresent invention provides for a relatively small release force andrelease motion, yet the output of the mechanism is a relatively largeforce acting over a relatively large movement. A mechanism according tothe present invention thereby provides a cost-effective way to providemechanical assistance in a folding seat, without requiring multipleinputs by a user and/or high input forces and/or large movements by auser.

In the foregoing description, it will be readily appreciated by thoseskilled in the art that modifications may be made to the inventionwithout departing from the concepts disclosed herein. Such modificationsare to be considered as included in the following claims, unless theseclaims by their language expressly state otherwise.

1. A folding seat assembly for motor vehicles, comprising: a supportstructure; a seat base structure movably mounted to the supportstructure for fore and aft movement relative to the support structurebetween a forward position and a rearward position, wherein the seatbase structure is biased towards the forward position; a seat backstructure pivotably mounted to the seat base structure for movementbetween a generally upright position and a folded position proximate theseat base structure, wherein the seat back structure is biased towardsthe folded position; a first releasable latch selectively retaining theseat base structure in the rearward position; a second releasable latchselectively retaining the seat back structure in the upright useposition; a control mechanism comprising; a housing; a pinion memberrotatably mounted to the housing for rotational movement between aretracted position and an extended position; a movable rack member thatmoves between a retracted position and an extended position, wherein therack member engages the pinion member such that movement of the rackfrom its retracted position to its extended position causes the pinionmember to rotate from its retracted position to its extended position; alock member that is movable between a locked position and a releasedposition, wherein the lock member operably engages at least one of therack members and the pinion members and prevents movement of the pinionmember from its retracted position to its extended position when thelock member is in its locked position, and wherein the lock memberpermits movement of the pinion member from its retracted position to itsextended position when the lock member is in its released position;first and second elongated flexible members operably connected to thepinion member such that the pinion member pulls on the first and secondelongated flexible members as the pinion member rotates in a firstdirection from its retracted position to its extended position, whereinthe first elongated flexible member is operably connected to the firstreleasable latch, and wherein the second elongated flexible member isoperably connected to the second releasable latch, whereby the pinionmember pulls on the first and second elongated flexible members andreleases the first and second releasable latches as the pinion membermoves from its retracted position to its extended position, such thatthe seat back moves from its upright position to its folded position,and the seat base structure moves from its rearward position to itsforward position.
 2. The folding seat assembly of claim 1, wherein: thelock member is biased towards the locked position; the movable rackmember is biased towards its extended position; and including: a resetmember operably connected to the seat back structure and the movablerack member such that the reset member moves the rack member from itsextended position to its retracted position as the seat back structuremoves to the folded position from the upright position, and the lockmember moves to its locked position upon movement of the rack member toits retracted position.
 3. The folding seat assembly of claim 2,wherein: the rack member comprises a plurality of linear teeth, and thepinion member includes a plurality of teeth arranged to define an arc ofa circle and engaging the linear teeth whereby linear movement of therack member causes the pinion to rotate.
 4. The folding seat assembly ofclaim 3, wherein: the arc extends less than three hundred and sixdegrees.
 5. The folding seat assembly of claim 3, wherein: the rackmember is slideably mounted to the housing for reciprocating motionalong a first axis; the lock member is slideably mounted to the housingfor reciprocating motion along a second axis that is transverse to thefirst axis.
 6. The folding seat assembly of claim 5, wherein: thecontrol mechanism defines an interior space, and wherein at least aportion of the rack member is disposed in the interior space when therack member is in its extended position, and wherein at least a portionof the lock member is disposed in the interior space when the lockmember is in its extended position and the rack member is in itsretracted position, such that the lock member prevents movement of therack member to its extended position when the lock member is in itsextended position.
 7. The folding seat assembly of claim 1, wherein: thepinion member defines an angular displacement as it rotates in the firstdirection, and wherein the first and second elongated flexible membersmove linearly as the pinion member rotates in the first direction, andwherein the movement of the first and second elongated members is anon-linear function of the angular displacement of the pinion member. 8.The folding seat assembly of claim 7, wherein: the first and secondelongated flexible members move at substantially the same rate atsubstantially the same times.
 9. The folding seat assembly of claim 8,wherein: the pinion member rotates about an axis and defines aconnection point that is spaced-apart from the axis; the first andsecond elongated flexible members are connected to a single output cablethat is connected to the pinion member at the connection point.
 10. Thefolding seat assembly of claim 9, wherein: the connection point on thepinion member is positioned such that linear movement of the first andsecond elongated flexible members as a function of the angulardisplacement is greater when the pinion member is at its retractedposition than when the pinion member is at its extended position. 11.The folding seat assembly of claim 10, wherein: the movable rack memberis biased to its extended position by a spring such that the pinionmember generates a force tending to rotate the pinion member in thefirst direction, and wherein the pinion generates a force on the outputcable that increases as the pinion member rotates in the firstdirection.
 12. The folding seat assembly of claim 1, wherein: the firstand second elongated flexible members release the first and secondreleasable latches, respectively, at about the same time.
 13. Thefolding seat assembly of claim 1, wherein: the first elongated flexiblemember releases the first releasable latch before the second elongatedmember releases the second releasable latch.
 14. The folding seatassembly of claim 1, wherein: the seat back structure defines an upperportion, and wherein application of a force in an upward and rearwarddirection on the upper portion of the seat back structure when the seatback structure is initially in a folded position causes the seat back torotate towards the upright position, and also causes the seat basestructure to move rearwardly from the forward position to the rearwardposition.
 15. A seat assembly, comprising: a support structure; a seatbase movably mounted to the support structure for movement between firstand second positions relative to the support structure; a seat backmovably connected to the seat base for movement between first and secondpositions relative to the seat base; a first latch selectively retainingthe seat base in its first position relative to the support structure; asecond latch selectively retaining the seat back in its first positionrelative to the seat base; a control mechanism configured to selectivelyrelease the first and second latches, the control mechanism comprising;a rotating member that is rotatable between first and second positionsabout an axis to define an angular displacement, and wherein therotating member is biased towards the second position; first and secondoutput members operably interconnecting the first and second latches,respectively, to the rotating member, whereby the first and secondoutput members move at a non-linear rate as a function of the angulardisplacement of the rotating member and selectively release the firstand second latches, respectively.
 16. The seat assembly of claim 15,including: a reset member operably interconnecting the seat back and therotating member such that movement of the seat back from the secondposition to the first position causes the rotating member to move fromits second position to its first position.
 17. The seat assembly ofclaim 16, wherein: the control mechanism includes a movable lock memberselectively retaining the rotating member in its first position.
 18. Theseat assembly of claim 17, wherein: the rotating member defines at leastone connection point that is spaced-apart from the axis of the rotatingmember, and wherein at least one of the first and second output membersis operably connected to the connection point such that the one outputmember moves longitudinally upon rotation of the rotating member. 19.The seat assembly of claim 18, wherein: the first and second outputmembers comprise first and second output cables that are interconnectedto a third output cable that is connected to the connection point of therotating member.
 20. The seat assembly of claim 15, wherein: therotating member generates a force acting on the first and second outputmembers that increases as the rotating member moves from its firstposition to its second position.
 21. The seat assembly of claim 15,wherein: the control mechanism releases the first and second latches atsubstantially the same time.
 22. The seat assembly of claim 15, wherein:the rotatable member comprises a pinion having a plurality of teeth, andthe control mechanism includes a rack having a plurality of teethengaging the teeth of the pinion, and a spring biasing the rack from afirst position to a second position.
 23. The seat assembly of claim 22,including: a reset cable operably interconnecting the seat back and therack such that the reset cable moves the rack to its first position uponmovement of the seat back from its second position to its firstposition.
 24. The seat assembly of claim 23, wherein: the controlmechanism includes a lock member that selectively retains the rack inits first position; and including: an input member that releases thelock member it permit movement of the rack from its first position toits second position.
 25. The seat assembly of claim 24, including: aspring biasing the lock member into a locked position wherein the lockmember prevents movement of the rack from its first position to itssecond position.